JP2578232B2 - Non-volume transfer rotary machine - Google Patents

Abstract

PCT No. PCT/FR89/00119 Sec. 371 Date Sep. 10, 1990 Sec. 102(e) Date Sep. 10, 1990 PCT Filed Mar. 17, 1989 PCT Pub. No. WO89/09342 PCT Pub. Date Oct. 5, 1989.A rotary machine, having non-positive, displacement, which can be used as a pump, compressor, generator or drive turbine wherein the rotor is form by a particular combination of paddles and blades which improves fluid flow through the rotary machine. The paddle and blade configuration of the rotor utilizes the Archimedes screw principal to enhance the fluid flow characteristics and resist cavitation in the rotor chamber.

Description

Description: TECHNICAL FIELD [0001] The present invention relates to a machine that uses kinetic energy and centrifugal force to perform transmission between work and fluid and vice versa.

[Conventional technology]

Known types of devices, such as screw propulsors, centrifugal turbines, spiral centrifuges, etc.
Well-known difficulties are encountered in trapping fluid, especially when the rotational speed is significantly increased. The term NPSH ("net net absorption head"), which defines the pump's utilization limits, describes the obstacles encountered. Archimedes screws of increasing diameter, known since the time of Leonardo da Vinci, are used in the form of a supercharged annulus and are the best known remedy to avoid cavitation of liquids or excessive pressure reduction of the incoming gas. It has become.

[Problems to be solved by the invention]

The machine forming the main part of the invention enables the above-mentioned problems to be solved for the following reasons. It is necessary to provide an opposing circular casing in which the fluid is introduced directly through the interior of the increased diameter Archimedes screw forming the rotor, guiding and compressing a long linear flow towards the rotor, Finally, it can be solved because the inlet and the leading edge of the guide element are made more aerodynamic with the new fluid circuit.

[Means for solving the problem]

The machine of the present invention is of the type comprising at least one hollow spirally wound vane and at least one paddle spatula disposed about the centerline of rotation of the machine. Both the spatula are housed in a circular casing surrounding the rotor from the outside, forming a fluid inlet and preventing the escape of fluid, the main features of the machine being:
A rotor comprising at least one paddle spatula disposed about a centerline of rotation and receiving at least one hollow spirally wound vane at a forward portion of an outer edge of the paddle spatula, A rotor, wherein the paddle-shaped spatula and the blades extend simultaneously in a diametrical direction and a longitudinal direction with respect to a rotation center line at different pitches, and a fluid compression element located upstream of the rotor and having a fluid escape. A circular casing forming a fluid inlet adapted to block and compress the fluid, said fluid being swept by the rotor blades along a peripheral flow on the one hand and paddles of the rotor on the other. And a circular casing that allows the spatula to flow as a central stream.

According to another feature of the invention, the shape of the rotating surface described by the passage of the leading edge of the vane is substantially parallel to or slightly behind the axis of symmetry on either side of the axis of symmetry. It is laterally delimited by a conical flat portion and is extended by a converging portion towards the front of the rotor.

Each paddle spatula merges with the blade at the root near the axis, so that the paddle spatula and the blade move instantaneously together.

The pitch of the blades decreases in a direction away from the axis.

The blades are provided with a peripheral edge that is curved in the direction of rotation of the rotor, and the blades, on the other hand, are bent as lips toward the rear of the rotor to provide an outer leading edge that enhances the passage of liquid peripheral flow. And, on the other hand, also has an inner edge curved as a lip toward the rear end of the rotor to help convert peripheral flow to central flow.

The rotor may include a paddle spatula confined to the space of the inner blades, and the leading edge of the rotor extends radially in the space between the bottom and top at the peripheral portion between the blades , So that the peripheral flow of the fluid flows backward.

The radiating portion of the blade is reduced or disappears at the front of the extension of the paddle spatula and grows again or reappears so that it is finally joined to the next paddle spatula.

The inside of the paddle is fixed to the rotor shaft, the diameter of the rotor being enlarged along its axis to form a closed or half-open turbine.

Under one preferred embodiment, the paddle spatula projects through the rear end of the rotor blades and the largest diameter and constitutes a centrifugal turbine, the end of which paddle spatula has An aft surface extends laterally outward and is at an angle to the axis of rotation at the same height as the turbine outlet.

In a first variant of the machine according to the invention, a circular casing surrounding the rotor from outside defines a fixed axial inlet in the direction of the rotor and at least one edge which provides a peripheral position for the fluid flow. One strip and one inside. The axial inlet can be fluid-
Fixed to the transport element.

In a second variant, the circular casing is rotatable, for example driven by a shaft passing through the rotor,
It also surrounds the rotor from the outside and defines a helical inlet with at least one twisted strip provided on the inside, the twisted strip being capable of distributing the kinetic energy and of the one or more strips. Through the streamlined shape, a circular peripheral fluid flow merges with the peripheral flow of the rotor.

In a third variant, the circular casing further comprises, in addition to the stationary axial inlet, a rotating impeller, which is driven, for example, by a shaft passing through the rotor and which is wound spirally. A paddle-shaped spatula whose inside matches the shape of the surface of the rotating body drawn by the passage of the leading edge of the rotor blades is provided, and the paddle-shaped spatula is limited to the space of the inner blade and the leading edge has a radius. Direction and over the peripheral portion between the vanes in the space located between the bottom and the top, allowing the peripheral flow of fluid to pass rearwardly, so that the overall axial inlet strip is The fluid flow is imparted with a circumferential flow so that the rotating impeller compresses the fluid flow and pushes it between its blades and the paddle spatula pushes the fluid flow through the rotor.

According to another feature of the invention, the circular casing is made up of completely circular elements, such as cylindrical rings, conical rings, holes, etc. at the largest diameter portion of the rotor blades.

The number of paddles in the rotor and the number of strips in the casing are different so as to eliminate harmonics generated by the flow of the resonating fluid.

The machine of the present invention may be provided with a diffuser disposed on the rear side of the rotor for guiding the fluid flow and most effectively utilizing the reaction force of the fluid flow.

A stationary chamber is provided, which surrounds the circular casing, protrudes forward and bends towards the interior of the circular casing, forming an injector supplemented or not supplemented by a stationary casing containing the entire machine, The edge of the end protrudes beyond the front and rear of the machine and bends inward to cover the whole and a second
And an outflow element for supplying fluid to the second injector to add an introduction effect to the fluid flowing into the rear end.

The one or more strips of the circular casing are located at a forward central portion away from the rotating surface described by the passage of the leading edge of the rotor blades, and ultimately define a central opening, especially in the absence of a shaft. Disappear.

A flat portion defined by the shape of the rotating surface (depicted by the passage of the leading edge) swept by the leading edge of the rotor blades, a circular element of a circular casing, and at least a rear portion of the rotor Any sealing ring, known per se, located at the front end of the flange of one half-closed centrifugal turbine, and also the rear bore of any stationary chamber, has a gap of facing and of a predetermined size. .

This type of machine can be used as a means of propulsion or force generation, and the passage of the centrifugal turbine is provided with an injector connected to a fluid source and / or an electrically operated electrode.

In an advantageous manner, the bearing of the fluid film provided with a recess communicating with the inlet of the pressurized fluid through an orifice or reduced cross section is arranged on the rear side of the rotor in the case of a rotating circular casing. In the bore of a known seal ring provided at the front of at least one half-closed centrifugal turbine provided, or in the case of a stationary circular casing with impeller, behind a fixed axial inlet. Positioned within the bore, the fluid film bearing is configured to center the rear end of the rotating casing or the rear end of the impeller, respectively.

The accompanying drawings are given for illustrative purposes only,
Also, it should not be construed as limiting the scope of the invention, and the machine intentionally and schematically uses basic geometric elements to facilitate understanding of highly complex shapes. Have been described. In practice, these shapes are softened and rounded to match and facilitate the passage of the fluid flow.

[Embodiment of the invention]

Referring to the drawings, the machine of the present invention is illustrated as follows.

Spiral paddle spatula 11. A spirally wound blade 12 is fixed in front of the spiral. This assembly is the rotor 10
To form Paddle spatula 11 and blades 12 are at the front end of rotor 10
To provide only the lowest number of ridges that disturb fluid flow at the center of the rotor 10.

The leading edge provided by the wings 12 covering the paddle spatula 11,
The diameter 15 increases in the direction of the arrow and at the same time advances in the longitudinal direction 13 as indicated by the arrow before catching and catching the linear flow escaping outward.

The opposing circular casing 14 surrounding the rotor 10 prevents the escape of fluid and compresses this fluid. This casing is provided for the purpose of obtaining a compression element. Paddle spatula 11 and feather
After 12 leaves, the fluid gets two distribution paths inside the rotor 10. That is, the fluid passes directly behind the rotor 10 and either occupies the space between the insides of the vanes 12 located on the diameter directly above, or escapes between the vanes 12. If the rear part of the rotor 10 is at least partially blocked, only the outward passage is left outside, but the circular casing 14 prevents the discharge and retreat of fluid, so that a local force which pushes fluid into the rotor 10 Target overpressure follows. These elements are the first and second
And in FIG.

The inflow of the linear flow becomes easier as the edge of the paddle-shaped spatula 11 and the blade 12 is formed in a shape along the direction of the flow of the fluid. Will be rushed into. The leading edge 50 of the paddle 11 extends between the vanes 12 and the rear escapes or joins into the fluid so that it can be spread toward a complementary element such as a flange. The outer leading edge 51 of the vane 12 has a sharp edge determined by a compromise between the intersection of fluid acceptance and rejection, and its outer edge 52 introduces outer fluid inward and inward. It is an element for guiding the flow. The body of the blade 12 located between the outer leading edge or outer lip 51 and the outer edge or inner lip 52 is preferably rearwardly convex and forwardly concave, wherein the outer lip 51 and the inner lip 52 are concave.
Is compensated by pushing the fluid along it. This is shown in FIGS. 4 and 6.

The shape of the rotator surface described by the rotation of the edge of the blade 12 has a flat portion 20 substantially parallel to the axis and located on the rear side of the rotor 10 and can form a seal with the ring located on the opposite side. To do. Said shape also converges towards the front part 21. A hemispherical shape is preferred, but a shape that is locally perpendicular to the axis of rotation is selected according to the shape of the cone or rocket tip or various factors of the problem to be solved. FIG. 5 shows an example of one shape.

In one particular arrangement, the rotor 10 has a paddle spatula 11 that is housed only in the inner blade space 60. These paddles extend radially between the blades 12 at the periphery. The paddle spatula holds the vanes 12 there between to facilitate fluid flow into the interior of the rotor 10 or to prevent linear flow from flowing toward the compression element of the circular casing.
FIG. 7 shows an arrangement of this type.

When the paddle spatula 11 extends beyond the rear of the blades 12 and the largest diameter, the rotor 10 can take advantage of centrifugal force and thereby create a centrifugal turbine 90. The end of the paddle spatula 11 discharges fluid outward. In one preferred arrangement, the end of the paddle spatula is located towards the rear part 91. The turbine is closed or opened and housed in the body, and the fluid is therefore discharged rearward. To take advantage of the concomitant reaction of fluid flow during rotation of the centrifugal turbine, it is likewise preferred that the end of the paddle spatula 11 be at an angle 92 to the axis of rotation. FIG. 10 shows such an example.

The pitch of the blades 12 decreases with distance from the axis, so that the velocity of the fluid is apparently greater at the center than the periphery of the casing 14 and the angle of the blades 12 corresponds to this velocity.

According to FIG. 14, the shaded part corresponds to the empty space, the radiating part of the blade 12 becomes smaller or disappears at the front part 71 of the extension of the paddle spatula 11 and becomes larger again at 72 or The paddle spatula 11, which reappears, is joined so that the rear surface of the paddle spatula fits better. The inner or rear part of the paddle 11 is fixed to a shaft whose diameter extends to form a kind of shield flange, thus creating an open or semi-open centrifugal turbine. The number of paddles 11 and the number of strips 101 are different to eliminate harmonics caused by the flow of the resonating fluid. A diffuser 130 is located at the rear of the machine to guide the fluid flow and to maximize the fluid flow reaction forces. This machine would not be efficient without a circular opposing casing 14. The stationary casing preferably has a forward axial inlet 100 containing a strip 101 forming an inner passage which is progressively inclined in the direction of rotation of the rotor.
One effective method is to locate the rear portion of the strip 101 of the rotor 10 away from the center and to eliminate the same portion of the strip 101 to define the opening 171. This opening is in fact directed to a center where the flow is usually least distributed to the incoming flow of fluid carried by the conduit. The strip 101 located closest to the axis has disadvantages greater than those expected from improved fluid guidance in this central part, due to the required structural precision. Strip 101 and rotor 1
The greater degree of freedom imparted to the fluid by the larger spacing between zero allows the fluid flow in the conduit formed by the strip 101 to be redirected inefficiently, but not efficiently. The stationary circular casing 14 is often included in a conduit and / or body that is secured to the fluid inlet element by, for example, a flange 102. An example of these arrangements is shown in FIG.

In the variant shown in FIG. 12, the circular casing 14 is rotatable and has a helical inlet 121 formed by a twisted strip 121. Round casing 14
Is driven, for example, by a shaft 120 passing through the rotor 10. When driven from the outside without a central shaft, the strip 122 of the rotating circular casing 14 opens at the center to facilitate the introduction of fluid into the preferred area. Strip 122 of the rotating circular casing 14 in the rear part 170
The spacing of the rotors and the spacing of the blades 12 of the rotor 10 are also measures that can increase the "hydraulic" isolation of the device.

A third embodiment of the circular casing 14 is shown in FIG. 13 and, starting from the front, comprises:

A stationary circular casing 14 with an axial inlet 100 as described above, preferably a shaft that can pass through the rotor 10
A rotary impeller 140 driven by 141 to cover the rotor 10 from outside.

The impeller 140 comprises:-a spirally wound vane of the same nature as the vane 12;-a similar paddle spatula 142 of the same self-evident nature as the paddle spatula 11 limited to the inner vane space 60.

Fluid enters the axial inlet 100 and is separated by a strip 101 of the stationary circular casing 14 that guides the fluid toward the periphery in the same direction as the direction of rotation of the impeller 140. The fluid is thus compressed and flows between the impeller blades 143 assisted by the paddle spatula 142 located in the space between the blades. This flow is provided to rotor 10 with the desired overpressure under impeller 140. Figures 7, 9, 11, and 13 show examples of embodiments of this scheme.

 The following additional points are noted.

There is a flat portion 20 near the top of the blade 12 of the rotor 10,
Also among the possible variants of the circular casing 14 are overlapping circular surfaces 151, holes, rings, etc., all of which can be provided with a seal with the aid of a controlled gap 181.

Similarly, a sealing ring 180, known per se, is provided in the front flange of the centrifugal turbine 90 and behind the impeller 140 and preferably in a hole in the stationary chamber 160 surrounding the circular casing 14 preferentially.

However, the seal provided between the circular surfaces of these small gaps is not entirely watertight and continues even if the leakage has intensive rolling. The stationary chamber 160 makes these leaks available and available by being reintroduced in front of the circular casing with the aid of the injector 161 bent back in front of the circular casing. This aspirated fluid is used by the injector 161 to facilitate the introduction of said fluid.
The benefits of the introduction effect brought by can be obtained.

The stationary casing 162 covering the whole machine has additional advantages as long as the second injector 163 can be added. The second injector seeks to obtain kinetic fluid at the outlet of the centrifugal turbine 90 with the aid of a leaching device 164, which is a type of inverted injector. Examples of such devices are Nos. 11, 12, and 13.
It is shown in the figure.

The machine can be used as a propulsion means by utilizing the force created by the pressure difference between the front and back surfaces. A major increase in output speed is obtained, for example, by introducing and igniting fuel with the aid of injectors 190 and electrodes 191 in the conduit of the centrifugal turbine. These injectors 190 and electrodes 191 can perform other functions, such as mixing fuel, changing local electrical conditions, and the like. These elements are described in FIG.

Finally, a hole located in front of the stationary axial inlet 100 containing the sealing ring 180 or impeller 140, known per se, located in front of the flange of the centrifugal turbine 90, is advantageously provided with a pressurized fluid. It receives a fluid film bearing constituted by a recess 200 provided by an opening 201 of a predetermined diameter. The purpose of using this fluid film bearing is to mechanically hold the rings in place with respect to each other, because the circular casing 14 is fixed to the shaft with a helical inlet 121 when rotating. Alternatively, the portion fixed to the shaft by being fixed to the shaft in the form of the impeller 140 is extremely deviated from the rear of the circular casing 14.

This assembly is therefore more conveniently held and the relative centering eliminates the detrimental friction phenomena. These various elements are shown in FIGS.

In each case, the present invention is not limited to the above embodiments, but encompasses all possible modifications without departing from the scope or spirit of the present invention. In particular, the addition of a cooling system to reduce the temperature of the recirculated fluid and all known arrangements for creating centrifugal pumps and compressors are supplemental and relevant to the present invention. is there. The structural strength of this type of machine is sufficiently enhanced by providing fillets that help to provide improved aerodynamic properties to the internal circuitry. Thus, while preserving the substance of the general nature of the machine described above, it will be understood that the present invention also encompasses the development of forms derived from known and essential laws of fluid mechanics and mechanical engineering.

The engineering of the machines, pumps, turbines, propulsors, etc. according to the invention is realized from molded materials or production tools, more particularly by using so-called one-off wax technology. The solution has also been adapted to initially assemble discrete components, such as plates or sheets bent by heat or pressure. Metals, composites, plastics and their hybrids are all used.

The machine of the present invention has applications suitable for any transfer of gaseous fluids, liquids or pastes. Vacuum pump,
Gas compressors and steam recompression have particular advantages. In general, any fluid with low positive suction or at equilibrium water vapor pressure offers potential applications. Due to the pressure difference and velocity difference created between the suction and return surfaces, the conversion of energy to force can be applied to whatever force is effectively applied to this machine: servo mechanism, pressure generation, mass This brings the possibility to use it for transportation and the like. The addition of the injector and the electrodes achieves the interaction between the elements brought about by the contact (fluid, fuel, oxygen carrier, electricity, etc.) and also makes this machine usable in particular as a propulsion or generator.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a bottom view of the machine of the present invention, FIG. 2 is a cutaway front view of the rotor and circular casing of the machine shown in FIG. 3 is a top view of the above machine, FIG. 4 is a diagram showing an example of a paddle-shaped spatula and a cross section of each corresponding portion, FIG. 5 is a diagram showing a type of a rotor having a flat portion at the rear, FIG. 6 is a front view, a top view, and a cross-sectional view of a corresponding portion of the blade. The front view shows how the pitch changes with an increase in the diameter. FIG. 7 is limited to the inner blade space. FIG. 8 is a cutaway front view and a plan view of a casing having a spiral inlet, FIG. 9 is a front view of a rotary impeller, and FIG. 10 is a paddle-shaped spatula. A bottom view of a rotor adapted as a centrifugal turbine with its ends facing backwards and at an angle to the axis of rotation; FIG. 11 is a cross-sectional view of a machine in which the circular casing is stationary and the strip is located away from the rotor and has disappeared from the center. FIG. 13 is a cross-sectional view showing a stationary chamber and casing having an electrode, an injector, an injector, a controlled gap seal, and a fluid film bearing, which are driven by a shaft passing therethrough, and FIG. 13 shows a fixed circular casing. FIG. 14 is a cross-sectional view showing a machine including a driven axial inlet, a rotating impeller driven by a shaft passing through a rotor, a controlled clearance seal, and a fluid film bearing. FIG. 15 is a front view of the twisted strip and a plan view from above, showing the radiating vanes of the child disappearing and reappearing.

10 ... rotor, 11 ... paddle spatula, 12 ... feather, 14 ... circular casing, 20 ... flat part, 21 ... front part, 50 ... front edge, 51 ... outside front edge (outside Lip), 52 ... outer edge (inner lip), 60 ... inner blade space, 90 ... centrifugal turbine, 91 ... rear, 100 ... axial inlet, 101 ... strip, 107 ... opening.

Claims (20)

(57) [Claims] 1. A non-positive displacement rotary machine that can be used as a pump, compressor, propulsion device, generator or drive turbine, comprising at least one hollow spirally wound vane and said rotary machine. At least one paddle spatula disposed about the centerline of rotation, the blades and paddle spatula both surrounding the rotor from outside to form a fluid inlet to prevent fluid escape. A paddle-shaped spatula (11) at a front portion of an outer edge of the blade (12).
And the paddle spatula (11) and the blade (12) extend at different pitches in the diametrical direction (15) and the longitudinal direction (13) with respect to the rotation center line, and the rotor (10) The circular casing (14) provided on the upstream side includes a fluid compression element, and the fluid compression element transfers the fluid along the peripheral flow compressed and held by the circular casing (14). The corresponding space available for the fluid to be flushed first by the child (10) in the direction of the rear part, said fluid being said rotor (10)
A non-positive displacement rotary machine, wherein the rotary machine is introduced by the blades (1) of the above and is caused to flow as a central flow. 2. The shape of the surface of the rotor, drawn by the passage of the leading edge of the blade (12), is substantially parallel to said axis on either side of the axis of symmetry or at the rear end of said rotor (10). 2. The method according to claim 1, wherein the transverse direction is delimited by a slightly conical flat part in the direction and extended by a part converging towards the front end of the rotor. 4. The non-positive displacement rotary machine according to claim 1. 3. The paddle-shaped spatula (11) is united (30) with the blade (12) at the root near the axis, so that the paddle-shaped spatula and the blade can move together instantaneously. The non-volume transfer type rotary machine according to claim 1 or 2, wherein: 4. The rotary machine according to claim 1, wherein the pitch of the blades (12) decreases in a direction away from the axis. 5. The paddle spatula (11) is provided with a peripheral edge (50) extending between the blades (12) and curved in the direction of rotation of the rotor (10). ) Has an outer leading edge (51) which is sloped as a lip toward the rear of the rotor (10) to enhance the inflow of the peripheral flow of fluid, and likewise provides a central flow of said peripheral flow. 5. A method according to claim 1, wherein the lip has a curved inner edge as a lip toward a rear end of the rotor to assist in converting the flow. Non-volume transfer type rotary machine. 6. The rotor (10) has an inner-blade space (6).
0) limited by a paddle spatula (11), the front end of the paddle spatula extending radially at the peripheral portion between the vanes (12) in the space between the bottom and the top, and The non-positive displacement rotary machine according to claim 5, wherein the flow is caused to flow backward. 7. The front portion of said paddle spatula (11) before the radiating portion of said vane (12) becomes larger or reappears and is finally connected to a subsequent paddle spatula. The non-volume transfer rotary machine according to claim 5, wherein the rotary machine becomes or disappears. 8. A closed or half-opened turbine in which the inside of a paddle spatula (11) is fixed to a shaft (81) of a rotor (10) and the diameter of the shaft (81) increases along the axis. 6. The method according to claim 5, wherein
Or the non-volume transfer type rotary machine according to 7. 9. A paddle spatula (11) protrudes from the largest diameter portion at the rear end of the blade (12) of the rotor (10) to create a centrifugal turbine (90). An end (91) extending laterally outwardly and having an end face passing through an outlet of the turbine facing rearward and being inclined with respect to the axis of rotation (92). From 5,
A non-positive displacement rotary machine according to one of claims 7 and 8. 10. A stationary circular casing which surrounds a rotor (10) from the outside and initially defines an axial inlet (100) in the direction of said rotor (10), the fluid of said circular casing being The compression element has at least one strip (101), said strip (101) being integrally fixed to said circular sealing and protruding shaped part of the rotating surface of said vane (12) or paddle spatula (11) Having a concave rear circular shape at least partially surrounding the fluid flow and imparting a peripheral location to the fluid flow, wherein said axial inlet (100) is secured to the fluid carrying element by a flange (102). The non-positive displacement rotary machine according to claim 1. 11. The number of paddle spatula (11) and strip (10)
11. The method of claim 10, wherein the number of 1) is different so as to eliminate harmonics caused by the flow of the resonating fluid.
4. The non-positive displacement rotary machine according to claim 1. 12. The circular casing (14) is rotatable, driven by a shaft (120) passing through the rotor (10), and the circular casing (14) extends the rotor (10) outward. A spiral inlet (121) consisting of said fluid compression element is defined and at least one twisted strip (122) is provided on the inside, said inner strip (122) being provided with a distributed kinetic energy and 2. The fluid compressed circular peripheral flow which merges with the peripheral flow of the rotor (10) via the streamlined shape of the inner strip (122). Non-volume transfer type rotary machine. 13. A method according to claim 1, wherein a diffuser is arranged at the rear of the machine for guiding the flow of the fluid and for maximizing the reaction force of the fluid flow.
13. The non-positive displacement rotary machine according to item 1 of 12. 14. The circular casing (14) further comprises, in addition to the stationary axial inlet (100), the axial inlet (1).
00) and the rotor (1) located between the rotor (10).
0), and a rotating impeller (140) driven by a shaft (141) penetrating the rotor (10).
A paddle-shaped spatula (142) carrying a spirally wound vane (143) conforming to the shape of the surface of the rotating body drawn by the passage of the leading edge of the blade (12), 14
2) is limited to the inner vane space such that the leading edge extends radially at the peripheral portion between the vanes (143) in the space located between the bottom and the top, and restricts the peripheral flow of fluid to the rear. And generally, the stationary strip (101) of the fluid compression element at the axial inlet (100) directs the fluid flow circumferentially and the impeller (140) directs the fluid flow. The paddle-shaped spatula (142) compresses and flows between the blades (143), and the fluid flows through the rotor (1).
(0)
12. The non-positive displacement rotary machine according to one of items 1,10 and 11. 15. The circular casing (14) has a fully circular element such as a cylindrical ring, conical ring, hole or the like at the part of the maximum diameter of the blade (12) of the rotor (10). 15. The non-positive displacement rotary machine according to claim 1, wherein the rotary machine is constituted by (151). A stationary chamber (160) surrounds the circular casing (14) and protrudes forward to form the circular casing (14).
Forming an injector (161) that is bent towards the interior of and is supplemented by a stationary casing (162) that houses the entire machine;
The edge of the stationary casing (162) projects beyond the front and rear of the machine and bends inward to cover the assembly and to have a second injector (163) at the front end and the second injector (163) at the rear end. 16. A fluid discharge element (164) for supplying a fluid to 163), wherein the fluid discharge element (164) is adapted to introduce a flow of fluid into the fluid discharge element. Non-volume transfer type rotary machine. 17. The rotor according to claim 1, wherein said strip (101, 142) of said circular casing (14) is provided at a front central portion thereof.
11) characterized in that it is located away from the surface of the rotating body described by the leading edge of 0) and eventually disappears so as to define a central opening (171).
16. The non-positive transfer rotary machine according to one of claims 15 to 15. 18. A flat part (20) defined by the shape of the surface of a rotating body drawn by passing a leading edge of a blade (12) of the rotor (10), and a circular element of the circular casing (14). (151), a seal ring (180) provided at a front end of a flange of at least half-closed centrifugal turbine (90) located behind the rotor (10), and a rear hole between the stationary chamber (160). The non-positive displacement rotary machine according to any one of claims 1, 2, 9, 14, and 15, characterized in that: 19. An injector (190) usable as a propulsion element and connected to a passage of said centrifugal turbine (90) to at least one of a source of fluid and an electrically operated electrode (191). 2. The device according to claim 1, wherein
Or the non-volume transfer rotary machine according to 9. 20. A fluid film bearing provided with a recess (200) communicating with an inlet of pressurized fluid via a reduced cross-sectional orifice (201) at least located behind the rotor (10). Either a hole in the seal ring (180) provided at the front end of the half-closed centrifugal turbine (90) or a hole provided behind the stationary axial inlet (100), 19. Non-volume transfer according to claim 9, 12, 14 and 18, characterized in that the rear end of the circular casing (121) or the rear end of the impeller (140) is centered. Rotary machine.